Element for metallic belt

ABSTRACT

An element  40  for a metallic belt in a belt-type continuously variable transmission has a structure in which: a belt radial outer portion  46   b  of a metallic belt  7  is linearly shaped to come into line contact with a pulley radial inner portion  11   a  which is a constant-angle inclined generatrix portion of a pulley  5  or  8;  a projecting portion  48  located below a locking edge portion  44   a  and extending inward in the belt radial direction is provided at each of the lower ends of both side edges of the element  40;  and when the element  40  and a pulley radial outer portion  11   b  which is a curved generatrix portion of the pulley  5  or  8  contact each other, the projecting portion  48  bends inward in the axial direction of the pulley  5  or  8.

TECHNICAL FIELD

The present invention relates to an element for a metallic belt wound around a drive pulley and a driven pulley in a continuously variable transmission.

BACKGROUND ART

A belt-type continuously variable transmission including a drive pulley, a driven pulley, and a metallic belt wound around the two pulleys is conventionally known (for example, see Japanese Patent Application Laid-Open No. H6-307510).

FIG. 7 shows a deviation Δe in longitudinal center line of a metallic belt 97 in a cross section including the center axes of a drive pulley 98 and a driven pulley 95, in the case where the contact surfaces (hereafter referred to as “V surfaces”) between the respective drive pulley 98 and driven pulley 95 and the metallic belt 97 in the cross section are linearly shaped. As shown in FIG. 7, when the gear ratio is changed from maximum (LOW ratio) through intermediate (MID ratio) to minimum (overdrive (OD) ratio), the metallic belt 97 moves in the direction of the center axes of the drive pulley 98 and driven pulley 95 according to changes in width of the pulley grooves of the two pulleys 98 and 95. Here, since the amount of movement of the metallic belt 97 differs between the drive pulley 98 side and the driven pulley 95 side, the deviation Δe in longitudinal center line of the metallic belt 97 changes in the right-left direction, and the orientation 99 of the metallic belt 97 fluctuates right and left (this deviation in longitudinal center line of the metallic belt 97 is hereafter referred to as “misalignment”).

If the metallic belt is misaligned in this way, uneven wear occurs in the contact surfaces (V surfaces) between the respective drive and driven pulleys and the metallic belt, or the metallic belt is twisted and as a result decreases in durability.

In Patent Literature 1, misalignment is prevented in the following manner. The inclination angle (the angle with respect to a plane perpendicular to the center axis of the pulley) of the generatrix on the outer diameter side of the pulley is set larger than the inclination angle of the generatrix on the inner diameter side of the pulley to widen the pulley groove, while the boundary portion between the outer diameter side and inner diameter side of the pulley is shaped as a smooth convex curved surface. The side edge of the body portion of each element of the metallic belt is formed in correspondence with the pulley in such a manner that the angle on the outer diameter side of the metallic belt is set to make line contact with the inner diameter side of the pulley and the angle on the inner diameter side of the metallic belt is set to make line contact with the outer diameter side of the pulley.

A continuously variable transmission in which the generatrix from the inner diameter side to outer diameter side of the pulley is a smooth curve to prevent misalignment is also known (for example, see Japanese Patent Application Laid-Open No. 2002-31215).

CITATION LIST Patent Literature

Patent Literature 1: Japanese Patent Application Laid-Open No. H6-307510

Patent Literature 2: Japanese Patent Application Laid-Open No. 2002-31215

SUMMARY OF INVENTION Technical Problem

In Patent Literature 1, the boundary portion is a smooth convex curved surface, but the amount of change of the angle of the generatrix in the boundary portion is large. This causes a problem in that gear change control when the element contacts the boundary portion is difficult.

In Patent Literature 2, the part of contact between the pulley and the element is point contact. This causes a problem in that the friction coefficient between the element and the pulley decreases in a small diameter state where the element contacts the inner diameter side of the pulley.

In view of the above, the present invention has an object of providing an element for a metallic belt in a continuously variable transmission capable of reducing misalignment while ensuring friction force between an element and a pulley in a small diameter state.

Solution to Problem

[1] To achieve the object stated above, the present invention is an element for a metallic belt used in a belt-type continuously variable transmission, the belt-type continuously variable transmission including: a drive pulley and a driven pulley each of which has a pulley groove defined by a fixed pulley half and a movable pulley half; and a belt including an element and wound around the pulley groove of each of the drive pulley and the driven pulley, a constant-angle inclined generatrix portion in which a generatrix is inclined at a constant angle to widen the pulley groove radially outward being formed on a radial inner side of a surface of contact, with the element, of at least the fixed pulley half out of the fixed pulley half and the movable pulley half, a curved generatrix portion in which the generatrix is curved to gradually increase an inclination angle while widening the pulley groove radially outward being formed on a radial outer side of the surface of contact, the belt-type continuously variable transmission changing a gear ratio by: moving the movable pulley half of one pulley out of the drive pulley and the driven pulley away from the fixed pulley half of the one pulley to increase a width of the pulley groove of the one pulley; and moving the movable pulley half of the other pulley out of the drive pulley and the driven pulley closer to the fixed pulley half of the other pulley to decrease a width of the pulley groove of the other pulley, and the element being formed with a locking edge portion that contacts an adjacent element; a belt radial outer portion of a side edge of the element is linearly shaped to come into line contact with the constant-angle inclined generatrix portion of any of the drive pulley and the driven pulley; a projecting portion located below the locking edge portion and extending inward in a belt radial direction is provided at each of lower ends of both side edges of the element; and when the element and the curved generatrix portion on the radial outer side of any of the drive pulley and the driven pulley contact each other, the projecting portion bends inward in an axial direction of the pulley.

According to the present invention, in the case where the belt is wound around the pulley in a small diameter, the constant-angle inclined generatrix portion of the pulley and the linear portion of the side edge of the element contact each other, where the element and the pulley are in line contact state. The present invention can thus prevent a decrease in friction coefficient in the case where the belt is wound around the pulley in a small diameter.

In the case where the belt is wound around the pulley in a large diameter, the widthwise outer side edge of the projecting portion contacts the curved generatrix portion of the pulley while bending. This prevents conventional local contact between the lower end of the side edge of the element and the pulley, thus improving the durability of the element and the pulley.

[2] Moreover, in the present invention, it is preferable that the projecting portion is formed so that a width of the projecting portion at a belt radial outer end is a predetermined width allowing the projecting portion to bend, and that the width is gradually increased inward in the belt radial direction.

With such a structure, the bendable projecting portion can be formed easily, and since the projecting portion gradually widened inward in the belt radial direction it is able to enhance durability of the projecting portion.

[3] Moreover, in the present invention, a widthwise outer side edge of the projecting portion may be linearly shaped to follow an extension line of the linearly shaped side edge of the element. With such a structure, the part of the element that comes into line contact with the constant-angle inclined generatrix portion on the radial inner side of the pulley can be extended to the projecting portion, which contributes to a larger friction force.

[4] Moreover, in the present invention, a widthwise outer side edge of the projecting portion may be a curved shape to be depressed inward in a width direction. With such a structure, when the projecting portion contacts the curved generatrix portion on the radial outer side of the pulley while bending, the curved shape portion of the projecting portion and the curved generatrix portion of the pulley come into line contact with each other easily. Hence, the friction force with the element can be enhanced on the radial outer side of the pulley, as well.

[5] Moreover, it is preferable that a radius of curvature of the curved shape of the projecting portion is equal to or greater than a radius of curvature of the curved generatrix portion of each of the drive pulley and the driven pulley. With such a structure, when the projecting portion bends, the curved shape portion of the projecting portion easily comes into line contact with the curved generatrix portion of the pulley in a relatively wide range. This facilitates stable line contact between the projecting portion and the pulley, and reduces the surface pressure to improve the durability of the element and the pulley.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is an explanatory diagram schematically showing a continuously variable transmission that uses an element according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram schematically showing part of a metallic belt according to the first embodiment.

FIG. 3 is an explanatory diagram showing an element according to the first embodiment.

FIG. 4 is an explanatory diagram showing a pulley and the element according to the first embodiment.

FIG. 5A and FIG. 5B are explanatory diagrams showing the state of the metallic belt wound around pulleys according to the first embodiment.

FIG. 6 is an explanatory diagram showing an element according to a second embodiment of the present invention.

FIG. 7 is an explanatory diagram showing misalignment in a conventional continuously variable transmission.

DESCRIPTION OF EMBODIMENTS

The following describes a first embodiment of an element for a metallic belt according to the present invention, with reference to FIGS. 1 to 5. FIG. 1 shows the overall structure of a belt-type continuously variable transmission 1 that uses an element according to the first embodiment. The belt-type continuously variable transmission 1 includes: a transmission input shaft 2 connected to an output shaft of an engine ENG as a drive source via a flywheel damper 10; a transmission counter shaft 3 arranged in parallel with the transmission input shaft 2; a metallic belt mechanism 4 placed between the transmission input shaft 2 and the transmission counter shaft 3; and a forward/backward switching mechanism 20 placed on the transmission input shaft 2. The belt-type continuously variable transmission 1 is provided with a hydraulic pump 30 and a gear change control valve 60. The hydraulic pump 30 transmits hydraulic oil to the gear change control valve 60 via an oil passage 30 c. The gear change control valve 60 is capable of adjusting/controlling the hydraulic pressure of the transmitted hydraulic oil. The gear change control valve 60 transmits the pressure-adjusted hydraulic oil to the metallic belt mechanism 4 via oil passages 30 d and 30 e. The gear change of the belt-type continuously variable transmission 1 is controlled in this way.

The metallic belt mechanism 4 includes: a drive pulley 5 provided rotatably on the transmission input shaft 2; a driven pulley 8 provided on the transmission counter shaft 3 so as to rotate together with the transmission counter shaft 3; and a metallic belt 7 wound around the two pulleys 5 and 8.

The metallic belt 7 includes: many circularly connected elements 40; and two bundles of ring 50 attached to the elements 40 in a stacked state, as shown in FIG. 2. Each element 40 is formed like a flat plate, and includes: a head portion 41 with an ear portion 42 extending right and left; a body portion 44 extending right and left over the ear portion 42; and a neck portion 43 connecting the body portion 44 and the head portion 41, as shown in FIG. 3.

A nose hole 41 a is formed on one surface of the head portion 41, and a nose portion 41 b that can be inserted into the nose hole 41 a of the adjacent element 40 is formed on the other surface of the head portion 41. The adjacent elements 40 are connected to each other by the nose portion 41 b of one element 40 being fit into the nose hole 41 a of the other element 40.

The body portion 44 is provided with a locking edge portion 44 a extending in the width direction, in its upper part. The body portion 44 also includes a projecting portion 48 extending downward from the position below the locking edge portion 44 a (inward in the belt radial direction), in each of the lower ends of both side edges.

The ring 50 is formed by radially stacking ring-shaped endless metallic bands. The ring 50 is located in the space defined by the ear portion 42, the neck portion 43, and the body portion 44 on the right and left of the element 40, and sandwiched between the lower edge of the ear portion 42 and the upper edge (a saddle surface 45) of the body portion 44. A V surface 46 is formed on both right and left side edges of the body portion 44 including the projecting portions 48. The V surfaces 46 contact and are sandwiched between V surfaces 11 of the drive pulley 5 or the driven pulley 8 which will be described later.

The drive pulley 5 includes: a fixed pulley half 5A provided rotatably but axially non-movably on the transmission input shaft 2; and a movable pulley half 5B axially movable relative to the fixed pulley half 5A. A drive-side cylinder chamber 6 is formed on the side of the movable pulley half 5B, and an axial thrust (drive pulley axial thrust) for axially moving the movable pulley half 5B is generated by the hydraulic pressure supplied from the gear change control valve 60 via the oil passage 30 d. A V surface 11 is formed in the part of contact (contact surface) of the fixed pulley half 5A with the metallic belt 7. The V surface 11 is also formed in the movable pulley half 5B so as to face the fixed pulley half 5A. The metallic belt 7 is sandwiched between the V surfaces 11 formed in the fixed pulley half 5A and the movable pulley half 5B.

The driven pulley 8 includes: a fixed pulley half 8A arranged joined onto the transmission counter shaft 3; and a movable pulley half 8B axially movable relative to the fixed pulley half 8A. A driven-side cylinder chamber 9 is formed on the side of the movable pulley half 8B, and an axial thrust (driven pulley axial thrust) for axially moving the movable pulley half 8B is generated by the hydraulic pressure supplied from the gear change control valve 60 via the oil passage 30 e. The V surfaces 11 are formed in the driven pulley 8 as in the drive pulley 5, and the metallic belt 7 is sandwiched between the V surfaces 11 in the fixed pulley half 8A and the movable pulley half 8B.

As shown in FIG. 4, a pulley radial inner portion 11 a of the V surface 11 is a constant-angle inclined generatrix portion in which the generatrix is inclined at a constant angle θ (where θ is an angle with respect to a plane perpendicular to the center axis of the pulley) so that a pulley groove 5C or 8C defined between the fixed pulley half 5A or 8A and the movable pulley half 5B or 8B widens radially outward. A pulley radial outer portion 11 b of the V surface 11 is a curved generatrix portion in which the generatrix is curved so that the pulley groove 5C or 8C gradually widens radially outward and the inclination angle gradually increases. The inclination angle of the outermost diameter of the V surface 11 as the contact range that contacts with the element 40 is θ′+Δθ where θ′=θ.

A belt radial outer portion 46 b of the V surface 46 which is the side edge of the element 40 is linearly shaped to follow the pulley radial inner portion 11 a of the V surface 11 as a constant-angle inclined surface of the pulley 5 or 8, and is set to have an inclination angle of θ. A belt radial inner portion 46 a of the V surface 46 as the side edge of the projecting portion 48 is linearly shaped to follow the extension line of the linearly shaped belt radial outer portion 46 b, and is set to have an inclination angle of θ, too. A plurality of oil drain grooves 47 extending in the plate thickness direction of the element 40 are provided in the V surface 46.

The gear change control valve 60 controls the hydraulic pressure (pulley pressure control hydraulic pressure) supplied to the drive-side cylinder chamber 6 and the driven-side cylinder chamber 9, as a result of which a pulley axial thrust (referred to as “slip prevention axial thrust”) for preventing the metallic belt 7 from slipping can be set, and the pulley widths of the drive pulley 5 and driven pulley 8 can be set variably. This enables the belt-type continuously variable transmission 1 to continuously change the winding radius of the metallic belt 7 on each of the pulleys 5 and 8 to steplessly (continuously) control the gear ratio.

The forward/backward switching mechanism 20 includes: a planetary gear set PGS; a forward clutch 24; and a backward brake 25. The planetary gear set PGS has a single pinion structure made up of: a sun gear 21 connected to the transmission input shaft 2; a ring gear 23 connected to the fixed pulley half 5A; and a carrier 22 that pivotally supports a pinion 22 a which meshes with the sun gear 21 and the ring gear 23 rotatably and revolvably.

The backward brake 25 is capable of fixing the carrier 22 to and holding it in a casing Ca. The forward clutch 24 is capable of connecting the sun gear 21 and the ring gear 23. When the forward clutch 24 is engaged, the sun gear 21, the carrier 22, and the ring gear 23 rotate together with the transmission input shaft 2, and the drive pulley 5 is driven in the same direction (forward direction) as the transmission input shaft 2. When the backward brake 25 is engaged, on the other hand, the carrier 22 is fixed to and held in the casing Ca, and the ring gear 23 is driven in the opposite direction (backward direction) to the sun gear 21.

The planetary gear set PGS may have a double pinion structure. In such a case, the fixed pulley half 5A is connected to the carrier, and the ring gear is provided with the backward brake.

Power from the engine ENG is transmitted to the transmission counter shaft 3 through gear change via the metallic belt mechanism 4 and the forward/backward switching mechanism 20. The power transmitted to the transmission counter shaft 3 is transmitted to a differential mechanism 29 via a start clutch 26 and gears 27 a, 27 b, 28 a, and 28 b, and then transmitted from the differential mechanism 29 separately to right and left wheels (not shown).

The gear change control valve 60 controls the hydraulic pressure supply to the drive-side cylinder chamber 6 and the driven-side cylinder chamber 9 to perform gear change control, as mentioned earlier. Here, the operation of the gear change control valve 60 is controlled by gear change control signals C_(DR) and C_(DN) from a gear change control unit 70.

The gear change control valve 60 has two solenoid valves for controlling the respective hydraulic pressures supplied to the drive-side cylinder chamber 6 and the driven-side cylinder chamber 9. These solenoid valves are operated according to the gear change control signals C_(DR) and C_(DN) output from the gear change control unit 70, for gear change control. The hydraulic pressures in the cylinder chambers 6 and 9 are set respectively based on the gear change control signals C_(DR) and C_(DN), thus setting the drive pulley axial thrust applied to the drive pulley 5 and the driven pulley axial thrust applied to the driven pulley 8.

For such gear change control, an engine rotation signal Ne, an engine throttle opening degree signal T_(H), a vehicle velocity signal V, a drive pulley rotation signal N_(DR) obtained by a drive rotation speed detector 71, and a driven pulley rotation signal N_(DN) obtained by a driven rotation speed detector 72 are detected and input to the gear change control unit 70.

The generatrix in the pulley radial inner portion 11 a of the V surface 11 of the pulley 5 or 8 is linearly shaped to form a constant-angle inclined surface, and the belt radial outer portion 46 b of the V surface 46 of the element 40 is linearly shaped to follow the constant-angle inclined surface of the pulley radial inner portion 11 a of the pulley 5 or 8. This ensures a sufficient friction coefficient μ between the pulley 5 or 8 and the metallic belt 7, and prevents the metallic belt 7 from slipping from the pulley 5 or 8. The reason is described below.

The friction coefficient μ between the V surface 11 of the pulley 5 or 8 and the V surface 46 of the element 40 is not constant. The friction coefficient μ increases when the V surface 11 and the V surface 46 are in line contact with each other, and decreases when the V surface 11 and the V surface 46 are in point contact with each other.

This is because the pulley 5 or 8 and the metallic belt 7 are not in direct contact with each other but a reaction film (boundary film) made of an additive in lubricating oil is present in the part of contact between the pulley 5 or 8 and the metallic belt 7. When the V surface 11 and the V surface 46 are in point contact with each other, the area of the part of contact is smaller than when the V surface 11 and the V surface 46 are in line contact with each other, so that the shear strength of the oil film between the V surface 11 and the V surface 46 decreases and the friction coefficient μ decreases. When the V surface 11 and the V surface 46 are in line contact with each other, the area of the part of contact is larger than when the V surface 11 and the V surface 46 are in point contact with each other, so that the shear strength of the oil film between the V surface 11 and the V surface 46 increases and the friction coefficient μ increases.

Thus, of the pulley radial inner portion 11 a and pulley radial outer portion 11 b of the V surface 11, the pulley radial inner portion 11 a in which the generatrix is linearly shaped is in line contact with the belt radial outer portion 46 b of the V surface 46 to increase the friction coefficient μ, and the pulley radial outer portion 11 b in which the generatrix is curved is in point contact with the belt radial inner portion 46 a of the V surface 46 to decrease the friction coefficient μ.

FIG. 5A shows the state of the metallic belt 7 when a gear ratio i is LOW. The winding radius of the metallic belt 7 is small on the drive pulley 5 side and large on the driven pulley 8 side. Accordingly, the number of elements 40 engaging with the drive pulley 5 is smaller than the number of elements 40 engaging with the driven pulley 8.

Transmission torque is given by the product of the friction force of each individual element 40, the number of elements 40 engaging with the pulley 5 or 8, and the distance between the axis to the winding position. On the drive pulley 5 side, the number of elements 40 engaging with the drive pulley 5 and the distance from the axis to the winding position are both small, which increases the friction force of each individual element 40. On the driven pulley 8 side, on the other hand, the number of elements 40 engaging with the driven pulley 8 and the distance from the axis to the winding position are both large, which decreases the friction force of each individual element 40.

Hence, whether or not a slip occurs between the pulley 5 or 8 and the metallic belt 7 depends on whether or not a sufficient friction coefficient μ between the pulley radial inner portion 11 a of the drive pulley 5 and the element 40 is ensured, while the friction coefficient μ between the pulley radial outer portion 11 b of the driven pulley 8 and the element 40 has little influence.

In this embodiment, the generatrix of the pulley radial inner portion 11 a of the drive pulley 5 is linearly shaped, and the belt radial outer portion 46 b and the belt radial inner portion 46 a, which is the side edge of the projecting portion 48, of the V surface 46 come into line contact with the pulley radial inner portion 11 a of the drive pulley 5 to increase the friction coefficient μ. This reliably prevents the metallic belt 7 from slipping. Moreover, even when the generatrix of the pulley radial outer portion 11 b of the drive pulley 5 is curved to compensate for misalignment, the metallic belt 7 is kept from slipping because the friction force required of each individual element 40 is small on the large diameter side.

FIG. 5B shows the state of the metallic belt 7 when the gear ratio i is OD. The winding radius of the metallic belt 7 is small on the driven pulley 8 side and large on the drive pulley 5 side. Accordingly, the number of elements 40 engaging with the driven pulley 8 on the small diameter side is smaller than the number of elements 40 engaging with the drive pulley 5 on the large diameter side.

Transmission torque is given by the product of the friction force of each individual element 40, the number of elements 40 engaging with the pulley 5 or 8, and the distance between the axis to the winding position. On the driven pulley 8 side, the number of elements 40 engaging with the driven pulley 8 and the distance from the axis to the winding position are both small, which increases the friction force of each individual element 40. On the drive pulley 5 side, on the other hand, the number of elements 40 engaging with the drive pulley 5 and the distance from the axis to the winding position are both large, which decreases the friction force of each individual element 40.

Hence, whether or not a slip occurs between the pulley 5 or 8 and the metallic belt 7 depends on whether or not a sufficient friction coefficient μ between the pulley radial inner portion 11 a of the driven pulley 8 on the small diameter side and the element 40 is ensured, and the friction coefficient μ between the pulley radial outer portion 11 b of the drive pulley 5 and the element 40 has little influence.

In this embodiment, the generatrix of the pulley radial inner portion 11 a of the driven pulley 8 is linearly shaped, and the belt radial outer portion 46 b of the V surface 46 comes into line contact with the pulley radial inner portion 11 a of the driven pulley 8 to increase the friction coefficient μ. This reliably prevents the metallic belt 7 from slipping. Moreover, even when the shape of the generatrix of the pulley radial outer portion 11 b of the drive pulley 5 is curved to compensate for misalignment, the metallic belt 7 is kept from slipping because the friction force required of each individual element 40 is small on the large diameter side.

In the continuously variable transmission 1 that uses the element 40 according to this embodiment, in the case where the metallic belt 7 is wound around the pulley 5 or 8 in a small diameter, the pulley radial inner portion 11 a as the constant-angle inclined generatrix portion of the pulley 5 or 8 and the V surface 46 of the side edge of the body portion 44 including the projecting portion 48 contact each other, where the element 40 and the pulley 5 or 8 are in line contact with each other in a relatively wide range.

In the case where the metallic belt 7 is wound around the pulley 5 or 8 in a large diameter, the pulley radial outer portion 11 b as the curved generatrix portion of the pulley 5 or 8 and the belt radial inner portion 46 a as the side edge of the projecting portion 48 contact each other, where both projecting portions 48 are sandwiched by the pulley 5 or 8 and bend inward in the width direction (inward in the axial direction of the pulley 5 or 8).

Therefore, the decrease in friction coefficient in the case where the metallic belt 7 is wound around the pulley 5 or 8 in a small diameter can be prevented by line contact in a relatively wide range including the projecting portion 48, and the decrease in durability of the pulley 5 or 8 and the element 40 caused by high surface pressure in the case of point contact can be prevented by line contact.

In the case where the metallic belt 7 is wound around the pulley 5 or 8 in a large diameter, the widthwise outer side edge of the projecting portion 48 contacts, while bending, the pulley radial outer portion 11 b as the curved generatrix portion of the pulley 5 or 8. This contributes to a relatively large contact area between the element 40 and the pulley 5 or 8, so that a relatively large friction force can be attained.

The projecting portion 48 is formed as follows: its width w at the belt radial outer end is set to a predetermined width allowing the projecting portion to bend, and the width is set either unchanged to the belt radial inner end or gradually increased inward in the belt radial direction so that W≧w where W is the width at the belt radial inner end. The bendable projecting portion 48 can thus be formed easily. Furthermore, gradually increasing the width inward in the belt radial direction further enhances the durability of the projecting portion 48.

In the case where the metallic belt 7 wound around the pulley 5 or 8 is in a small diameter, the side edge of the element 40 and the pulley radial inner portion 11 a of the pulley 5 or 8 come into line contact with each other. Here, a failure to properly discharge lubricating oil present between the element 40 and the pulley 5 or 8 causes a fluid lubrication state and the metallic belt 7 may slip more easily.

If the oil drain groove 47 extending in the plate thickness direction of the element 40 is formed in the linearly shaped radial outer portion, i.e. the belt radial outer portion 46 b and the widthwise outer side edge of the projecting portion 48, of the side edge of the element 40, the lubricating oil between the element 40 and the pulley 5 or 8 is properly discharged (released) from the oil drain groove 47, so that the metallic belt 7 can be prevented from slipping.

The following describes an element 40 for a metallic belt according to a second embodiment of the present invention, with reference to FIG. 6. The element 40 for a metallic belt according to the second embodiment has the same structure as in the first embodiment, except that the widthwise outer portion of the projecting portion 48 is a curved shape.

A radius of curvature r of the curved shape of the projecting portion 48 is set to be equal to or greater than a radius of curvature R of the pulley radial outer portion 11 b as the curved generatrix portion of the pulley 5 or 8 (R≦r). Hence, in the case where the metallic belt 7 is wound around the pulley 5 or 8 in a large diameter, the projecting portion 48 bends inward in the width direction, and the belt radial inner portion 46 a of the side edge of the projecting portion 48 contacts the pulley radial outer portion 11 b of the pulley 5 or 8 in a relatively wide range. The element 40 for a metallic belt according to the second embodiment can thus obtain a relatively large friction force even in the case where the metallic belt 7 is wound around the pulley 5 or 8 in a large diameter.

DESCRIPTION OF REFERENCE NUMERALS

1: belt-type continuously variable transmission

2: transmission input shaft

3: transmission counter shaft

4: metallic belt mechanism

5: drive pulley

5A: fixed pulley half

5B: movable pulley half

5C: pulley groove

6: drive-side cylinder chamber

7: metallic belt

8: driven pulley

8A: fixed pulley half

8B: movable pulley half

8C: pulley groove

9: driven-side cylinder chamber

10: flywheel damper

11: V surface

11 a: pulley radial inner portion (constant-angle inclined generatrix portion)

11 b: pulley radial outer portion (curved generatrix portion)

21: sun gear

22: carrier

22 a: pinion

23: ring gear

24: forward clutch

25: backward brake

26: start clutch

27 a, 27 b, 28 a, 28 b: gear

29: differential mechanism

30: hydraulic pump

30 c, 30 d, 30 e: oil passage

40: element

41: head portion

41 a: nose hole

41 b: nose portion

42: ear portion

43: neck portion

44: body portion

44 a: locking edge portion

45: saddle surface

46: V surface

46 a: belt radial inner portion (curved shaped)

46 b: belt radial outer portion (linearly shaped)

47: oil drain groove

48: projecting portion

50: ring

60: gear change control valve

70: control unit

71: drive side rotation speed detector

72: driven side rotation speed detector

Ca: casing

C_(DR), C_(DN): gear change control signal

ENG: engine

PGS: planetary gear set

Ne: engine rotation speed signal

T_(H): engine throttle opening signal

V: vehicle velocity signal

N_(DR): drive pulley rotation signal

N_(DN): driven pulley rotation signal 

1. An element for a metallic belt used in a belt-type continuously variable transmission, the belt-type continuously variable transmission including: a drive pulley and a driven pulley each of which has a pulley groove defined by a fixed pulley half and a movable pulley half; and a belt including an element and wound around the pulley groove of each of the drive pulley and the driven pulley, a constant-angle inclined generatrix portion in which a generatrix is inclined at a constant angle to widen the pulley groove radially outward being formed on a radial inner side of a surface of contact, with the element, of at least the fixed pulley half out of the fixed pulley half and the movable pulley half, a curved generatrix portion in which the generatrix is curved to gradually increase an inclination angle while widening the pulley groove radially outward being formed on a radial outer side of the surface of contact, the belt-type continuously variable transmission changing a gear ratio by: moving the movable pulley half of one pulley out of the drive pulley and the driven pulley away from the fixed pulley half of the one pulley to increase a width of the pulley groove of the one pulley; and moving the movable pulley half of the other pulley out of the drive pulley and the driven pulley closer to the fixed pulley half of the other pulley to decrease a width of the pulley groove of the other pulley, and a locking edge portion that contacts an adjacent element is formed in the element; a belt radial outer portion of a side edge of the element is linearly shaped to come into line contact with the constant-angle inclined generatrix portion of any of the drive pulley and the driven pulley; a projecting portion located below the locking edge portion and extending inward in a belt radial direction is provided at each of lower ends of both side edges of the element; and when the element and the curved generatrix portion on the radial outer side of any of the drive pulley and the driven pulley contact each other, the projecting portion bends inward in an axial direction of the pulley.
 2. The element for a metallic belt used in a belt-type continuously variable transmission according to claim 1, wherein the projecting portion is formed so that a width of the projecting portion at a belt radial outer end is set to a predetermined width allowing the projecting portion to bend, and that the width is gradually increased inward in the belt radial direction.
 3. The element for a metallic belt used in a belt-type continuously variable transmission according to claim 1, wherein a widthwise outer side edge of the projecting portion is linearly shaped to follow an extension line of the linearly shaped side edge of the element.
 4. The element for a metallic belt used in a belt-type continuously variable transmission according to claim 1, wherein a widthwise outer side edge of the projecting portion is a curved shape to be depressed inward in a width direction.
 5. The element for a metallic belt used in a belt-type continuously variable transmission according to claim 4, wherein a radius of curvature of the curved shape is equal to or greater than a radius of curvature of the curved generatrix portion of each of the drive pulley and the driven pulley. 